Train braking system



Jan. 19, 1937. E. E. HEWITT TRAIN BRAKING SY'STEM .Filed Nbvi 3, 1954' 4 Sheets-Sheet 1 'w INVENTOR ELLIS E HEWITT BY QM. 4%

ATTOR Y 7 Jan. 19, 1937. E. E. HEWITT TRAIN BRAKING SYSTEM Filed Nov. .3, 1934 v 4 Sheets-Sheet 2 I INVENTOR ELLIS E. HEWITT BY ATTORNEY Omv WOW v VOD 7 mm 7 mwh mwm QQN Fm wow W KL m @0 bwwm,

Jain. 19,1937. E. E. HEWITT, 2,068,337

I TRAIN BRAKING SYS'ISEM Fil ed Nov. 5, 19:54

4 Sheets-sheaf, s

Patented Jan. 19, 1937 UNITED STATES PATENT OFFlCE 2,068,337 TRAIN BRAKING SYSTEM Application November 3, 1934, Serial No. 751,340

29 Claims.

My invention relates to braking equipment for railway vehicles and is particularly adapted for use on high speed traction vehicles driven by electric motors.

1 In the operation of high speed trains andsimilar vehicles it is desirable to provide a brake equipment having ample braking capacity to take care of the most rigid requirements the equipment will be called upon to meet. It is well known that for a given braking pressure friction type brakes are less effective in retarding the motion of a vehicle at high speeds than at low speeds because the coefiicient of friction between the rubbing parts is lower at high speeds than at low speeds. In order to bring a vehicle to a stop quickly it has been the usual practice for an operator to apply the brakes with a high degree of braking pressure at the high speeds and as the speed of the vehicle decreases to so operate the brakes as to cause the braking pressure to be decreased in such manner that the vehicle is brought to a stop quickly and smoothly without dangerous shock or skidding of the wheels.

Because of the difficulty of properly reducing the braking pressure at the desired rate it becomes desirable, in many instances, to provide a retardation controller for regulating the degree of application of the brakes. This may comprise an inertia responsive device, such as a pendulum, that assumes various positions in accordance with variations in the deceleration of the vehicle, and is adapted, by means of electric circuits or otherwise, to control the degree of application of the brakes. .13 A desirable type of brake equipment to use with high speed traction vehicles and railway trains is one employing both a brake for providing braking force to the wheels of'a vehicle and a braking effect directly applied to the rails. The brake for applying a braking torque to the wheels of the vehicle may be the Well known fluid pressure brake, an electric brake, or a combination of the two, while the track brake may be a magnetic brake controlled either by fluid pressure, electrical means, or by a combination of both means. In such an equipment a greater braking effect can be produced by operation of both the wheels and track brakes than can be obtained by operation of either of them alone.

It is an object of my invention to provide braking equipment for railway vehicles in which a plurality of braking means are provided that are controlled from a common brake controlling device in accordance with a desired degree of braking.

It is another object of myinvention to provide a retardation controlled braking system in which the braking pressure is automatically controlled by a retardation controller that is manually adjusted toprovide a desired degree of retardation during a service operation of the brakes, and that is automatically adjusted to provide a greater rate of retardation upon an emergency operation of the brakes.

It is a further object of my invention to provide a braking system in which an electric brake and a fluid pressure brake are employed and in which the retardation controller is employed for controlling one of said brakes in accordance with the rate of retardation of the vehicle.

It is a still further object of my invention to provide a retardation controlled braking system in which an electric braking means and a fluid pressure braking means are employed, and in which deadman devices are employed for causing application of the brakes.

It is a further object of my invention to provide a retardation controlled braking system which is provided with safety control mechanism for automatically applying the brakes to effect a rate of retardation of the vehicle to a value that is greater than normal service application of the brakes upon failure of safety control pipe pressure.

Other objects and advantages of my invention will be apparent from the following description of one preferred embodiment thereof when taken in connection with the accompanying drawings in which Figs. 1, 2 and 3, when placed end to end from left to right, together constitute a diagrammatic view illustrating circuits and apparatus comprising one preferred embodiment of my invention.

Fig. 4 is a diagrammatic sectional view of the self-lapping brake valve device shown in Fig. 2.

Fig. 5 is a sectional view taken on the line 5 -5 of Fig. 2 and Fig; 6 is a diagrammatic development of the control drum and earns of the brake controlling device illustrated in Fig. 1.

Referring to the drawings, and more particularly to Figs. 1, 2 andv 3 thereofin which brake apparatus is illustrated as employed in accordance with my invention on two train units, the apparatus comprises brake cylinders l and r 2 by means of which the brakes are applied upon the flow of fluid under pressure thereto, as supplied by a feed valve device 3, from a main reservoir las controlled by a relay valve device 5 that is governed in accordance with the operation of a self-lapping brake valve device 6 for controlling the supply of fluid under pressure to and from the application and release pipe I, either in accordance with the operation of the brake controlling device 8, or in accordance with the operation of a deadman relay valve device 9, upon a predetermined reduction in pressure in. the safety control pipe II. A retardation controller I2 is provided for controlling the degree of application of the fluid pressure brakes to limit the rate of retardation of the vehicle to a desired value by operation of the magnet valve devices l3 and I4 that are interposed between the brake valve device 6 and the relay valve device 5.

The braking equipment also includes magnetic track brake mechanism employing the track shoes l5, I6, I! and I8 and a dynamic braking equipment wherein the vehicle driving motors 2|, 22, 23 and 24 operate as electric generators for supplying current to the dynamic braking resistor 25.

The brake controlling device 8 comprises a casing 26 enclosing a contact carrying drum 2'! carried on a shaft 28 provided with a handle 29 for manual operation. At the lower end of the shaft 28, cams 3| and 32 are provided for controlling the operation of the fluid pressure brake in accordance with the position of the handle 29.

The contact carrying drum 2! is provided with conducting segments 33, 34, 35, andv36. The conducting segment 36 controls the lowering and the raising of the magnetic track shoes into and out of engagement with the track rail, the conducting segment 34 controls the supply of current to the magnetic track shoe windings, and the conducting segment 33 controls the energization of the windings of the track shoe brakes in a manner to be later explained. The conducting segment 35 controls the interruption of power to the vehicle driving motors upon movement of the brake controlling handle 29 to a brake applying position, and also controls the application of the dynamic brakes.

In the lower part of the casing 26 an emergency valve chamber 3'! is provided that is in constant communication with the safety control supply pipe II that is supplied with fluid under pressure from the main reservoir pipe 41 in a manner to be later explained. An emergency valve 42 is provided within the chamber 31 and is urged by a spring 43 to the seat 44 to close communication from the safety control pipe I I to the atmosphere through the exhaust port 38. 'The emergency valve 42 is provided with a stem 45 that is adapted to be engaged by the cam 3| when the handle 29 is placed in the pneumatic emergency position to force the valve 42 from its seat 44 thus effecting communication from the pipe II to the atmosphere through the exhaust port 38.

A lever 4! is pivotally mounted on the pin 48 in the lower end of the casing 26, and is provided with an upper curved end for engaging the face of the cam 32, the lower end of the lever being pivotally attached to one end of a cable 49, the other end of which is attached to an operating lever 5| of the brake valve device 6, that is attached to the shaft 52 and is provided at its upper end with a spring 53, one end of which engages a lug 54 for biasing the lever 5i and the shaft 52 in a counterclockwise direction.

The brake valve device 6, best shown in Figure 4 of the drawings, may correspond to that disclosed and claimed in United States patent of Ewing K. Lynn and Rankin J. Bush for improiiments in Brake valve devices, No. 2,042,112 and assigned to the same assignee as this application.

The brake valve device 6 comprises a main body portion 55, a valve portion 56, a bracket portion 5'! and an emergency portion 58. The valve portion, the main body portion and the emergency portion together define a pressure chamber 59 that is in open communication, through the pipe and passage GI and the application and release pipe 1, with the piston chamber of the relay valve 5. The magnet valve devices l3 and 14 are interposed between the pipes BI and l to regulate the pressure of fluid acting on the piston of the relay valve device 5 in accordance with the rate of retardation of the vehicle.

The valve casing portion 56 is provided with a supply valve chamber 62 to which a feed valve device of the usual type supplies fluid under pressure at a reduced pressure from the main reservoir 4. .A supply valve 64 is contained with in the supply valve chamber 62 and is slidably disposed within the bushing sleeve 65 to engage a seat 66 carried by the valve portion of the casing. The valve 64 is subject to the pressure of a spring 67, one end of which engages the valve and the other end of which engages a nut 68 screw-threadedly attached within a bore in the valve portion of the casing.

The valve portion or section 56 of the casing is also provided with a cylinder 1| which is open at one end to the pressure chamber 59, the other end of the cylinder being closed by an adjusting member12 screW-threadedly attached within a bore in the casing section. The adjusting member 12 is provided with a central bore 73 which at its outer end is tapped to receive a screw-threaded cap member 74.

Operatively mounted in the cylinder H, adjacent to its open end, is a movable abutment in the form of a piston I5 having a stem 16 which is slidably guided by the adjustable member 12 within the inner end of the bore 13.- At one end of the piston 75 is a chamber 11 which is constantly open to the atmosphere through passage and pipe 18. A coil spring 19 is contained in the chamber 11 and is interposed between and engages 'the inner face of the piston 15 and the inner face of the adjusting member 12.

A release valve chamber 86 is provided within the piston 15 and is in open communication with the pressure chamber 59 through a passage 8|. A release valve 82 is contained within the valve chamber and is adapted to seat on a valve seat 83 formed on the piston and which is operative to'control communication between the valve chamber 89 and the chamber 1! through connecting passages84 in the piston stem 16. The release valve is provided with a stem 85, the small end of which slides within the bore in the stem of the piston 15 and the larger end of which is provided with a collar 66 which slidably engages the piston within a central bore 3'! and is subject to the pressure of the release valve spring 88 interposed between the engaging collar 86 and an annular flange 89 on the piston. Outward movement of the release valve relative to the piston '15 is limited by the collar 86 which engages a stop plate 99 that is secured to the piston I5. V

A mechanism is provided for controlling the operation of the supply valve 64 and the release valve 82 comprising spaced levers 91 that are pivotallymounted intermediate their ends on a pin 92 supported in a plunger 93 that is slidably guided within a bore 95 in the casing portion 56.

The upper ends of the spaced levers 9| are connected together by a pin 95 which is loosely mounted within a roller 95 that is adapted to operatively engage the outer end of the release valve stem 55. The lower ends of the spaced levers iii are connected together by a pin 91 on which one end of an operating rod 58 is pivotally mounted, the opposite end of the rod operatively engaging supply valve 64 within a recess 99 formed in its face.

For the purpose of operating the plunger 93 toward the right there is provided an operating lever IiH which is loosely mounted on the shaft 52 that is supported in the main casing section 55. Secured to the shaft 52 is an intermediate lever I82 provided with a lug I555 which overrides the lever liil so that when the shaft 52 is rotated in a clockwise direction the lug H13 engages the lever Ifll to cause it to move the floating pivot carrier or plunger 93 to the right. A stop N34 is provided to limit the backward movement of the lever Iill.

When the shaft 52 and the lever till are in their release position as shown in Figure 4, the spring 57 forces the supply valve 5 1 to its seated position and the spring 58 forces the release valve 82 toward the left to its unseated position. It will be appreciated that the force of the release valve spring 88 is less than the force of the supply valve spring 51 which is less than the force of the regulating spring id.

The emergency portion 58 is provided with a block IE5 secured to a rod H35. One end of the rod I is connected to a piston Iii'l positioned within the piston chamber H33, through which communication is effected from the piston chamber of a sanding valve device M5 to the atmosphere through the passage W9, a choked port i l I and the exhaust passage l I2, when the piston lill' is in its illustrated position, The sanding valve device 5 id communicates with the pressure chamber 59, through the passage I55, when the rod I05 and block m5 are urged to the left by a spring lid. The other end of the rod lilii slidably interfits with a bore I id in a guiding member H5.

For normally maintaining the rod Hi6 and the block H35 in its illustrated position, a piston H5 within a piston chamber Ml is provided, the piston chamber being connected by passage and pipe IE8 and the choke i it?! to the main reservoir pipe M. So long as the pressure within the piston chamber H? is substantially equal to the pressure within the main reservoir pipe ll the piston i I6 is urged against the piston IEVE sufficiently to maintain the rod m5 and the block IE5 in their illustrated position against the pressure of the spring H4.

The relay valve device 5 comprises a casing having a piston chamber I2I constantly connected to the application and release pipe l and con taining a piston I22 which is adapted, through the medium. of a stem I23, to operate a slide valve I2 1, that is o-peratively connected to the stem and contained in a valve chamber I25 that is constantly connected to the brake cylinders l and 2 through a brake cylinder pipe I26. Also contained in the casing is a fluid pressure supply valve ml which is subject to the pressure of a spring I28 and which is provided with a stem I29 that is adapted to be operatively engaged by the end of the piston stem I23.

The relay valve device 5 is shown with the relay piston I22 and the slide valve I24 in their extreme left or brake releasing positions. With the slide valve I24 in this position, the valve chamber I25, and consequently, the brake cylinders I and 2, are connected to the atmosphere through an exhaust passage I3l. With the piston I22 in release position the stem I23, will be out of engagement with the end of the supply valve stem I29 so that the pressure of the spring l28 will maintain the supply valve I2l seated against its seat rib I32, thereby maintaining communication closed from a chamber I30, that is constantly connected to the main reservoir 4 through a main reservoir pipe 4|, to the valve chamber l25.

The deadmans relay Valve device 9 comprises a casing having a valve chamber I 33 that is in constant communication with the safety control pipe it, and which contains a spring-weighted valve piston I34 that is urged to its seat I35 by a spring I35. A chamber i3! is provided below the valve piston I34 about the seat rib I35 that is in constant communication with the piston chamber l I? through pipe and passage H8. The chamber IE2 is also connected to the chamber I33 through a restricted passage I351. The valve piston I34 is subject on its upper side to the pressure of the spring I36 and to the pressure within the chamber E33 which corresponds to that in the safety control pipe II, and, on its under side, to the pressure within the chamber I31 which, when the valve is seated, corresponds to the pressure within the main reservoir pipe 4|. Upon a decrease in pressure within the safety control pipe II below a predetermined amount the pressure in the chamber I3? will be sufiicient to raise the valve piston fist from its seat thus venting the piston chamber ill in the emergency portion of the brake valve device 6 through pipe H8 and exhaust port E38 until a sufficient reduction in pressure is eiiected to permit the valve I34 to again seat.

The retardation controller I2 comprises a casing enclosing an inertia device or pendulum I46 that is pivotally supported on the pin MI and positioned between the spring pressed plungers i 52 and I4? that resist movement of the pendulum Mil from its vertical position, and upon the lower end of which is mounted a movable contact member l 44 for engaging the fixed contact members M5 and I45 to control the magnet valve devices it and M. The plunger I42 extends through an opening at the inner end of a cylindrical portion l i'l of the casing structure and is provided with a flange M8 within the cylindrical portion for limiting the movement of the plunger I42 toward the pendulum. The plunger I42 is urged toward the pendulum by a spring I49, one end of which engages the plunger I42 and the other end of which terminates within a recess in, and is in engagement with the inner wall of, a cap I5I that extends through a central opening in the other end of the cylindrical portion I41 of the casing structure. A sleeve I 52 is slidably mounted within the cylindrical portion I41 of the casing structure and is provided with an inwardly extending flange I55 that is adapted to be engaged by the outwardly extending flange I48 of the plunger 542. The sleeve H52 is urged inwardly by a spring I54 positioned within the cylindrical portion I41 of the casing, and about a central guide wall portion 55 between the outer end of the cylinder and the end of the sleeve I52.

Upon movement of the pendulum I40 toward the left sufficiently to urge the plunger I42 against the bias of the spring I49, until the flange I48 of 7 the plunger I42 engages the flange I53 of the sleeve I52, the movable contact member I44 engages the contact member I45 causing energization of the winding of the magnet valve device I3.

Upon the application of a suflicient greater force the pendulum I49 will urge the plunger I42 toward the left, moving the sleeve I52 against the pressure of the spring I5 4 until the flange I53 on the inner side thereof engages the end of the guide wall I55, which acts as a stop, and the movable contact member I44 engages the contact member I46 to energize the winding of the magnet valve device I4.

In order to provide for adjusting the force of the spring I49 against the plunger I42 a lever I56 is provided, and is pivotally supported intermediate its ends on the pin I51 carried by the casing. The lower end of the lever I56 engages the outer face of the cap I5I, and the upper end of the lever I56 engages the face of a cam I58 attached to the lower end of a rod I59, that is manually adjustable by a lever I6I.

In order to provide for changing the setting of the retardation controller upon a reduction in pressure in the safety control pipe II a lever I62, mounted on the pivot pin I63, is provided having its upper end in engagement with the outer faceof the cap I5I, and pivotally connected by the pin I 64, at a point intermediate its ends, to a piston I65, sli-dably mounted within a piston chamber I66. The piston 565 is subject on one side to the force of a spring I61, and on'the other side to the pressure within'the piston chamber I66, which corresponds to the pressure in the safety control pipe I I. When the pressure within the safety control pipe I I, andwithin the piston chamber 66, is insufiicient to overcome the pressure of the spring I 61, it becomes effective to force the lever i2 toward the right against the bias of the spring I49, thus increasing its force.

Referring to the magnet valve devices I3 and I4 that are controlled by the retardation controller I2 and are interposed between the pipe BI and the application and release pipe 1 the magnet valve device I 3 comprises a magnet I68 operatively connected to a valve I'II for controlling communication between the chamber I12, that is constantly connected to the pressure chamber 59 of the brake valve device 6 through pipe and passage 6!, and the valve chamber I13 that is in communication with the piston chamber I2I of the relay valve device 5 through passage I14 and the application and release pipe 1. A spring I16 is provided within the chamber I 12 for urging the valve I'll from its seat. The release magnet valve device I4 comprises a magnet I69, operatively connected to a release valve I11 within the release valve chamber I15 connected to the passage I14, for controlling the release of fluid under pressure from the piston chamber I2I through the application and release pipe 1, the valve chamber I15, and the exhaust port I18, to the atmosphere. A spring I19 is provided within the release valve chamber I15 for urging the release valve I11 to its seat.

Mechanism is provided for operating the magnetic track shoes I5 and I9 into and out of engagement with the track rail I89, and comprises a track shoe raising magnet valve device I8I, a relay valve device I32, and track shoe raising cylinders I83 are provided.

Similar mechanism is provided for operating the magnetic track shoes I1 and I8.

The magnetic track shoe cylinders I83, as best shown in Fig. 5, are attached to the car body I84 and each cylinder is provided with a piston chamber I85 containing a piston I86 having a stem I81 that is connected to supporting bracket I88 connected to the track shoe I6 by any suitable means such as the pin I89. A pipe I9I is connected to the chamber I85 below the piston I86 for supplying fluid under pressure thereto to raise the piston and the track shoe from the rail. The other end of the pipe I9 I communicates with a valve chamber I92 within the relay valve device I82 containing a valve I93 that is adapted to engage the seat rib I 94 to close communication between the chamber I92 and an exhaust chamber I95, that is in open communication with the atmosphere through exhaust passage I96. The valve I93 is provided with a downwardly extending stem I91 that extends through a bore in the wall separating the chambers I92 and I95. A spring I98 is provided within the chamber I92 for forcing the valve I93 downwardly against its rib seat I94. The valve I93 is provided with a bore containing a needle valve I99 in its upper end for closing communication between the valve chamber I 92 and an inlet chamber 29I in the upper part of the relay valve device casing, that is in open communication with the main reservoir pipe M.

The relay valve device I82 is also provided, in its lower end, with a piston chamber 292 containing a piston 283 provided with an upwardly extending stem 294 for engaging the lower end of the valve stem I91. The piston chamber 292 is in open communication, through passage and pipe 2 I9, with an intermediate chamber 285 provided in the casing of the track shoe raising magnet valve device I8I. The magnet valve device I8I also includes a magnet 290 operatively connected to a release valve 286 contained within a release valve chamber 231 that is in open communication with the atmosphere through exhaust port 298 for controlling communication between the piston chamber 202 and the atmosphere. The valve 296 is provided with a downwardly extending stem 209 that engages an upwardly extending stem 2| I of a supply valve 2I2 positioned within a supply valve chamber 2I3, that is in open communication with the main reservoir pipe 4I. Aspring 2I4 within the valve chamber 2I3 urges the valve 2I2 to its seat, and the valve 296 from its seat.

The magnet 209 of the track shoe raising magnet valve device I8I is energized from a source of energy, such as the battery 2I5, to efiect the lowering of the magnet track shoes into engagement with the rail, either upon engagement of the conducting segment 36 of the brake controlling device 8 with the contact members 2I6 and 2 I 1; or upon operation of an automatic safety control switch 2| 8 to its circuit closing position upon a reduction in safety control pipe pressure below a predetermined amount. The circuit for energizing the magnetic track shoes extends from the overhead line conductor 2l9,

through the trolley 22I, conductor 222, track shoe line switch 223, conductor 224, one of the control relays 225, 226, 221, 228 or 229 to conductor 23!, the windings of the magnetic track shoes I 5 and I 6 to ground at 232, and through the windings of the magnetic track shoes I1 and I8 to ground at 233. One or more of the brake controlling resistors 234, 235, 236 and 231 may be included in this circuit depending upon through which of the relays 225 to 229 inclusive the circuit is completed. The track brake line switch 223 is operated to its circuit closing position,

either upon engagement of the conducting segment 34 of the brake controlling device 8 with the conducting contact members 238 and 239, or upon closing of the safety control automatic switch 239 upon a reduction in safety control pipe pressure. A safety control automatic switch 249 is also provided for operating the relay 229 to its circuit closing position upon a predetermined reduction in safety control pipe pressure thus effecting full energization of the track shoe magnet.

A line circuit breaker 24] and a power controller represented by the contact members 242 and 243 are provided for controlling the supply of power to the motors 2|, 22, 23 and 24 from the trolley 22l. .A contactor 244 is also provided for controlling the application of the dynamic brakes.

The apparatus also includes a deadman feature which comprises a controller handle device 245 and a diaphragm foot valve device 246 for effecting an emergency application of the brakes upon a reduction of pressure in the safety control pipe II. A cut-off valve device 241 is provided for preventing operation of the deadman feature provided the brakes have been applied sufficiently to provide a predetermined brake cylinder pressure. A conductors valve 248 is also provided for venting the safety control pipe II to effect an emergency application of the brakes. A reduction in pressure in the safety control pipe H from any cause effects an emergency application of the pneumatic brake through operation of the deadman relay valve device 9 and the brake valve device 6, and an emergency application of the electrical track brake through operation of the automatic pressure switches 2l8, 239 and 249 in a manner to be later explained.

The controller handle device 245 may comprise a handle 252, fastened on the pin 253 in the controller handle train, and provided with outwardly extending bifurcated fingers 254 that engage the head of a pin 255 to move the pin upwardly as the handle 252 is pressed down, thus raising the pin 255 against the pressure of a spring 256, and bringing it out of engagement with the lever 251. The lever 251 is pivotally mounted on a pin 258 in the casing of the controller handle device and its shorter end engages a valve stem 259 that extends upwardly to a double beat pilot valve 25l that is pressed downwardly by a spring 262 in the valve chamber 263. When the pin 255 is raised from engagement with the lever 251 the spring 262 forces the pilot valve 26l to its lower seated position to close communication between an exhaust port 264 and the valve chamber 263. that is in open communication, through pipe 265, with the chamber 261 of the foot pedal device 246, and effects communication between the valve chamber 263 and a chamber 266 that is constantly connected to the main reservoir pipe 4|.

The foot valve device 246 comprises a casing provided with the aforementioned chamber 261 and a valve 268 that is adapted to engage the seat rib 269 to control communication between the chamber 261 and a chamber 21! that is in open communication with a pipe 212 having two branches, one of which terminates in the check valve 213 and the other of which is connected to the cut-off valve device 241. When pressure is maintained on the foot pedal 214 the valve 268 is held in its seated position closing communication between the pipes 265 and 212. When pressure on the foot pedal 214 is released the spring 215 forces the foot pedal upwardly unseating the valve 268.

The cut-off valve device 241 is provided with a valve 216 for controlling the flow of fluid under pressure from a supply valve chamber 211, that is in open communication with the safety control pipe H, and a chamber 218 that is in open communication with the pipe 212. The chamber 218 is in communication with the chamber 218 of the foot valve device 246 through pipe 212.

The cut-off valve device is also provided with a diaphragm 219 which is adapted to cause the valve 216 to be seated when the pressure in the chamber 28E above the diaphragm 219 exceeds that acting upon the under side of the valve 216. The pressure above the diaphragm 219 is controlled by a control valve 282 which is urged toward a lower seat 263 by a spring 294, and toward an upper seat 285 by the pressure below the valve.

When the control valve 282 is positioned against its lower seat the chamber 29l, above the diaphragm 219, is in communication with the atmosphere through a passage 286 past the open upper seat 235 of the valve 292. A chamber 281, below the valve 282, is in constant communication with the brake cylinder pipe I26.

When the pressure within the chamber 281 which corresponds to brake cylinder pressure reaches a predetermined amount the control valve 282 is forced upwardly from its lower seat 283 against its upper seat 285 cutting off communication between the chamber 28! and the atmosphere and effecting the supply of fluid under pressure at brake cylinder pressure to the cham-- ber 28L When the fluid pressure above the diaphragm 219 reaches a predetermined value the valve 216 will be seated thus closing communication between the chambers 211 and 218, thus preventing the flow of fluid under pressure from the safety control pipe II to the chamber 21I in the foot valve device.

A conductors valve device 248 may comprise a casing containing a chamber 29! that is. in constant communication with the safety control pipe II. A valve 292 is contained within the chamber 29I for controlling communication between chamber 29! and chamber 293, that is connected through the exhaust port 294, to the atmosphere. The valve 292 is normally biased upwardly to its seated position by a spring 295 thus closing communication between the safety control pipe II and the atmosphere. A valve stem 296 extends upwardly from the valve 292 and engages a valve lever 291 pivoted on a pin 299 mounted on the valve casing. An operating lever 299 is pivotally mounted upon a pin 39! carried on a bracket extending upwardly from the valve casing and which when moved in either direction forces the valve lever 291 downwardly unseating the valve 292 and permitting fluid under pressure to be vented from the safety control pipe II to the atmosphere through the exhaust port 294.

Each of the automatic pressure control safety switches 239, 249 and 2|8 are alike in construction and comprise a casing enclosing a piston chamber 392 that is in open communication with the safety control pipe H and contains a piston 393 that is urged downwardly by a spring 394 above the piston. A stem 395 extends upwardly from the piston through the casing and carries a contact member 396 that is adapted to be moved to a circuit closing position upon the downward movement of the piston 393 by the spring 394 upon the release of pressure from the piston ha ber 392.

In order to provide for maintaining the desired pressure within the main reservoir 4 a compressor set 3| I is provided, the operation of which is controlled by a pressure responsive governor 3|2 that is effective upon a predetermined decrease in pressure within the main reservoir to operate a switch closing a circuit from the trolley through conductors 222 and 3|3, the motor 3|4 of the compressor set through a variable resistor 3| 5 to ground at 3|6. In order to provide for charging the battery 2I5 when the compressor set is in operation a charging battery switch 3|? is provided, the operating circuit of which is completed from conductor 3I3 through the resistor 3I8 to ground at 3I9, when the compressor circuit is energized. Upon closing of the battery charging switch 3| 1 the grounded terminal 32! of the compressor motor 3 I 4 is connected through conductor 322, the contact members of the switch 3|1, and conductor 323 to the positive terminal of the battery 2I5, thus connecting the battery 2I5 between the terminal 32I and ground in parallel circuit relation to the resistor 3I5. The voltage applied to the battery 2I5 will therefore correspond to the voltage drop across the resistor 3I5, and by varying the resistor 3I5 the voltage impressed upon the battery 2|5 may be correspondingly varied.

The operation of the braking system will now be described. The various parts of the apparatus are illustrated in their brake release position, and in this position the equipment is charged by the flow of fluid under pressure from the main reservoir 4 through pipe 40 past the feed valve device 3 to the main reservoir pipe 4| at a reduced pressure. From the main reservoir pipe 4| fluid under pressure flows to the control valve chamber of the relay valve device 5. Fluid under pressure also flows from the pipe 4| through the choke M9 to the chamber I31 in the deadman relay valve device 9 and, after the pressure in the chamber I33 has built up sufficiently to maintain the valve piston I34 in its seated position, to the piston chamber H1 in the emergency portion of the brake valve device 6 forcing the pistons H6 and W1, the rod I66, and the block I05 to the right, against the bias of the spring II4. Fluid under pressure also flows from the main reservoir p'ipe 4| to charge the lower valve chamber 2I3 of the track shoe raising magnet valve device I 8| and to the track shoe raising cylinders I83 through chamber of the relay valve device I82, past the needle valve I99, through valve chamber I92 and pipe I9I.

The safety control pipe II is initially charged with fluid under pressure from the main reservoir pipe 4| through chamber 266 in the controller handle device with the handle 252 in its depressed position, past pilot valve 26I in its lower position, through pipe 265, past valve 268 of the foot valve device in its unseated position, through pipe 212, and either through check valve 213 to the safety control pipe II, or through chamber 218 of the cut-off valve device 241, past valve 216 in its unseated position, through chamber 211 to pipe II. After pressure has built up in the safety control pipe II sufflciently to maintain the valve piston I34 of the deadmans relay valve device 9 seated, the safety control pipe will also be charged in part by the flow of fluid under pressure through the restricted passage I39, which is sufiicient to maintain the pipe I I charged against normal leakage when pressure on the lever 214 of the foot valve device 246 maintains the valve 268 in its seated position.

,Fluid under pressure flows from the safety control pipe II to the piston chamber I66 in the retardation controller thus compressing the spring I61 and relieving the pressure exerted thereby through the lever I62 against the cap I5I, so that the setting of the retardation controller is determined solely by the position of the handle I6I. Pressure must now be maintained on the foot valve device lever 214 or on the handle 252 of the controller handle device 245 in order to prevent venting air from the safety control pipe I I to the atmosphere, unless the brakes are applied with sufficient brake cylinder pressure, which is communicated to'the chamber 26E of the cut-off 'valve device 241, to force the diaphragm 219 down and cause the valve 216 to seat. The piston chambers 302 of the automatic pressure switch devices 2|8, 230 and 246 are charged with fluid under pressure from the safety control pipe II thus forcing the piston 363 and the contact members 306 to their upper or illustrated positions.

With the brake controlling device 8 in its release position, a circuit is completed from the positive terminal of the battery 2|5 through conductor 324, contact member 325, conducting segment 35, and contact member 326 of the brake controlling device 8, conductor 321, the winding of the line circuit breaker 24I, conductor 328 to the negative terminal of the battery 2I5, thus operating the line circuit breaker 24| to its circuit closing position. A circuit may now be completed through the motor controller, represented by the contact members 242 and 243, that extends from the overhead line conductor 2I9, through trolley 22I, conductor 222, the line circuit breaker 24I, conductor 329, the controller contact members 242 and 243, conductor 33| to a junction point 332, and from there to ground through twobranch circuits, one branch circuit extending through armature windings 333 and 334, respectively, of the motors 2| and 22, and through field windings 335 and 336, respectively, of motors 23 and 24, to the grounded terminal 331, and the other branch circuit extending from the junction point 332 through field windings 338 and'339, respectively, of motors 2i and 22, and armature windings 34| and 342, respectively, of motors 23 and 24, to the grounded terminal 331. It will be noted that the motor circuit .is completed through the line circuit breaker MI, and that this circuit breaker is maintained in its circuit closing position only when the brake controlling device 8 is in its brake release position, so that, upon movement of the handle 29 to any brake applying position, the circuit through the conducting segment 35 and the contact member 326 will be interrupted, causing the line circuit breaker 24| to drop to its circuit interrupting position and interrupt the flow of power to the motors 2|, 22, 23 and 24, regardless of whether the controller handle device 245 has been operated to its power oif position.

If the operator wishes to apply the brakes, the handle 26 of the brake controlling device 8 is moved from its release position. Upon the initial movement from release position the contact member 326 separates from the conducting segment 35 interrupting the circuit through the -winding of the line circuit breaker 24I, which tion. Upon movement of the handle 29 from release position through the first pneumatic service zone of the brake equipment, to the controller position indicated by the vertical line I in Fig. 6, the outer face of the cam 32 on the lower portion of the shaft 28 advances against the upper end of the lever ll. The lever 41 is thus actuated in a clockwise direction about the pivot pin '23, the lower end of the lever moving the cable 52 toward the left, thus moving the lever 55, shaft 52 and the operating lever I9I in a clockwise direction and forcing the plunger 93 toward the right. The first portion of this movement eifects a compression of the spring 88, and the seating of the release valve 82, closing communication between the pressure chamber 59 and the atmosphere through the passages SI, 22 and I8. Further movement of the plunger 93 toward the right causes the spaced levers 9| to pivot about their upper ends, further movement of the roller 96 being prevented by the regulating spring I9, and causes the rod 98 to force the supply valve 66 against the compression of the supply valve spring 61 to open communication between the main reservoir pipe 4i and the pressure chamber 59, through passage II and the supply valve chamber 62, thus supplying fluid under pressure from the main reservoir 4 through passage and pipe BI, the application and release pipe I to the piston chamber I2I of the relay valve device 5.

The amount of fluid under pressure supplied to the pressure chamber 59, and to the piston chamber I2I of the relay valve device 5 is dependent upon the degree of movement of the operating lever ml, and of the plunger 93, from their release positions, since, while the pressure within the chamber 59 increases due to flow of fluid thereto through the supply valve 64, a pressure is exerted on the chamber side of the piston I5 in opposition to the pressure exerted by the regulating spring I9. This pressure continues to build up until it becomes sufficient to force the piston I5 toward the right relieving the pressure on the roller 96 and permitting the supply valve spring fill to force the rod 98 toward the left pivoting the levers about the pivot pin 92 and moving the supply valve 64 into engagement with its seat 69. The amount of pressure on the chamber side of the piston I5 necessary to effect suflicient movement of the piston I5 to cause the supply valve 64 to seat is dependent upon the amount of movement of the operating lever I9I and of the plunger 93 from their release positions. The greater the movement of the operating lever IBI from its release position the greater will be the movement of the pivot pin 92 toward the right, and consequently, the greater will be the compression of the regulating spring I9 necessary to permit movement of the lever 9| and of the rod 98 to effect the seating of the supply valve 64. It will be apparent, therefore, that the brake valve device is self-lapping on a pressure basis, the degree of fluid pressure within the pressure chamber 5-9 necessary to effect the movement of the valve to lap position being dependent upon the degree of movement of the operating lever IllI from its release position.

Fluid under pressure thus supplied to the piston chamber ill of the relay valve device 5 causes the relay piston i22 to move toward the left carrying the slide valve I24 with it. As the relay piston and slide valve are thus operated the slide valve laps the release port I3I closing communication from the relay slide valve chamber I25 to the atmosphere. After the port I3I is lapped the end of the piston stem I23 engages the stem I29 of the supply valve I21 and causes this valve to be unseated from its seat rib I32 against the pressure of the spring I28. With the supply valve I21 unseated fluid under pressure is supplied from the main reservoir 2 through the feed valve 2 at a reduced pressure, through the main reservoir pi e 4 I, valve chamber I39, past the unseated valve I2'I through slide valve chamber I25 and brake cylinder pipe I26 to the brake cylinders I and 2.

With the relay and valve in this position a force is exerted to move the piston I22 and the valve H24 away from the supply valve I2! that consists of the pressure within the slide valve chamber I25 plus the pressure of the spring I28. The pressure within the slide valve chamber I25 is not immediately effective against the rear of the piston I22 because of the provision of a phantom piston 35I between which and the piston I22 a chamber 352 is provided connected to the slide valve chamber I25 through a restricted opening; 3553. Upon an increase or decrease in pressure within the slide valve chamber I25 the flow of fluid under pressure through the opening 259 between the chambers 952 and I25 causes the pressure within the chamber 352 to become equal to that within the valve chamber I25 after a slight time interval. When the pressure in the chamber 352 builds up to substantially the pressure on the face of the piston I22, as supplied throughthe application and release pipe I, the piston is moved away from the supply valve I 2'I sufficiently to permit it to seat and cut off communication between the main reservoir pipe 4i and the brake cylinders I and 2. When the supply valve I2I seats the spring I29 no longer is effective to force the valve stem I29 against the piston stem I23 so that the piston I22 and slide valve I 24 do not move further or sufiiciently to unlap the release port I3I. Fluid under pressure is therefore retained in the valve chamber I25 and in the brake cylinders I and 2 that is substantially equal to the pressure in the application and release pipe i.

If the operator now wishes to release the brakes the brake controller handle 29 is moved to its release position thus operating the cam 32 to relieve the pressure against the upper end of the lever 41 which is forced toward the left by the spring 53 on the brake valve device 6 operating through the lever 5| and the cable 59. This movement rotates the shaft 52 in a counterclockwise direc tion and relieves the pressure of the operating lever Iii! against the end of the movable plunger 93 which is forced toward the left by the supply valve spring 6! and the release valve spring 88 acting on the lower and upper ends, respectively, of the space levers 9!. Upon movement of the plunger 93 toward the left the release valve 22 will be moved to its unseated position by the spring 88 to effect communication between the pressure chamber 59 and the atmosphere through passage 8|, release valve chamber 89, passages 94, chamber 11 and the exhaust passage it.

The release of fluid under pressure from the pressure chamber 59 of the brake valve device 5 also eliects the release of fluid under pressure from the piston chamber I2I of the brake valve device 6 thus descreasing the pressure on the face of the piston I22 which is moved toward the left by the pressure in the valve chamber I25 and in the chamber 352, carrying the slide valve 22 with it until communication is effected between the slide valve chamber I25 and the atmosphere through the exhaust port I3I thus effecting the release of fluid under pressure from the brake cylinders I and 2 through the exhaust port I3I to release the brakes.

If the operator, after effecting the first pneumatic service application of the brakes as described above, wishes to make a further application of the brakes, the brake valve controller handie 23 is moved further from its release position. During movement of the controller handle 29 from the position indicated by the vertical dot and dash line I on Fig. 6 to the position indicated by the line 3, the portion of the face of the cam 32 that engages the lever 41 is of such shape that the lever 41 is not moved further in a brake applying direction but is retained in the position occupied when the controller handle 29 is in the position I of Fig. 6, thus maintaining the pneumatic brake applied with a brake cylinder pressure corresponding to that effected when the brake controller handle 29 is in position 1 of Fig. 6. I 7

When the'handle 29 of the brake controller 8 is moved to the position 2 on Fig. 6' the conducting segment 36 bridges the contact members 2I6 and 2H, the conducting segment 34 bridges the contact members 234 and 235, and the conducting segment 33 bridges the contact members 354 and 355. V

The controller segment 36, in this position, completes a circuit from the positive terminal of the battery 2I5 through conductor 324, contact members 2| I and H5 and the conducting segment 35, conductor 356, through the winding of the magnet 200 of the track shoe raising magnet valve device I8I, and by conductor 35i to the negative terminal of the battery 2 I5, thus energizing the winding of the magnet 238 to move valve 286 to its seat. As the valve 236 is seated, communication from the piston chamber 232 of the relay valve device I82, through the exhaust port 288, is closed and the valve 2I2 is forced from its seat thus effecting communication from the main reservoir pipe 4|, through valve chamber M3, the chamber 205, and the pipe 2I8, to the piston chamber 232 of the relay valve device I32. The supply of fluid under pressure to the piston chamber 202 causes the piston 203 to be moved upwardly. The piston stem 284 engages the valve stem I91 forcing the needle v-alve I39 to its seat to close communication from the main reservoir pipe M to the track shoe raising cylinders I 83 through chambers 2!, I92 and pipe I95, and forcing the valve I93 from its rib seat I34 to open communication from the cylinders to the atmosphere through pipe ISI, cham- I32 and I95, and the exhaust port I96. Upon the release of fluid under pressure from the piston chamber I85 of the track shoe raising cylinders I83, the track shoes I5, I6, I! and I8 are moved downwardly by gravity into engagement with the rail I80.

In this position of the controller drum 2! a circuit is also completed from the junction point 358 of the motor circuit through conductor 359, the winding of the track brake line switch 223, conductor 35I to the junction point 362 and through conductor 363, contact member 238, conducting segment 34 and contact member 239 to ground at 354, and to the grounded terminal 33? of the motor circuit, thus impressing across the winding of the track brake line switch 223 the voltage or counter-electromotive force of the motor armatures 34I and 342 in series which, so long as the vehicle is in motion, will energize the winding of the line switch 223 to maintain it in its circuit closing position to close a circuit from the overhead trolley wire 2I9, through the trolley 22I, conductor 222, the contact members of the line switch 223 conductor 224 to the contact member 354 on the brake controller 8. In the assumed, or first track brake applying position of the controller 8 this circuit is completed. to ground through the conducting seg ment 33, the contact member 355 and the winding of the relay 225, thus actuating the relay 225 to its circuit closing position to complete a circuit from the conductor 224 through the contact members of the relay 225, the resistors 234, 236, 231, and the conductor 23I, through the windings of the track shoes I5 and I6 to ground at 232 and through the windings of the track shoes I? and I8 to ground at 233. As the controller handle 29 is moved further from its release position the conducting segment 33 engages successively the conducting members 365, 366, 367 and 368 which complete circuits to ground through the windings of relays 226, 227, 228 and 229, respectively, shunting the resistors 234, 235,

and 23?, respectively, from the circuit energizing the windings of the track shoes thus increasing the degree of energization of the track shoe magnets step by step. As the controller drum 2? is moved away from its release position and the several conducting contact members 355, 355, 366 and 36? have completed circuits for effecting the closing of their associated relays 225, 223, 22? and 223, these contact members are separated from the conducting segment 33, leaving only the lower relay 229 in its circuit closing position.

As the controller drum 2'! is moved further away from its release position or from position 3 to position 5 on the diagram of Fig. 6, the magnetic track brake remains fully energized and the cam 32, which is so shaped that its outer face extends further from the shaft 28 as indicated bythe upwardly sloping surface from position 3 to position 5 in the lower part of the diagram in Fig. 6, effects a further clockwise movement of the lever 41 about the pin 48 through the second pneumatic service application zone. This movement of the lever 41 effects a corresponding movement of the lever 5| and of the operating lever IOI of the brake valve device 3 to efiect a further increase in pressure within the pressure chamber 59 and within the piston chamber I2! of the relay valve device 5 to effect a corresponding increase in the pressure within the brake cylinders I and 2.

When the controller drum 2'! reaches position 4 on the diagram in Fig. 6, the conducting member 369 engages the conducting segment 35 completing a circuit from the positive terminal of the battery 255 through conductor 324, contact member 325, conducting segment 35, contact member 363, conductor 3'II, the winding of dynamic braking contactor 244, conductors 328 and 351 to the negative terminal of the battery 255 thus closing the dynamic braking contactor 244. The contactor 244, upon being energized, closes a dynamic braking circuit extending from the junction point 358 of the motor circuit through conductor 359, the contact of the dynamic braking contactor 244, the rheostat arm 322, the dynamic braking resistor 25 and conductor 313 to the junction point 314 of the motor circuit. I am aware that in dynamic braking systems of the character herein illustrated means is provided for automatically moving the rheostat arm 3'12 along the variable resistor 25 in such manner as to maintain the dynamic braking effect upon the motors 2|, 22, 23 and 24 substantially constant while their speed, and consequently their counter-electromotive force is decreasing. Since, however, such mechanism forms no part of the present invention is it not illustrated or described.

An emergency operation of the brakes may be effected by placing the handle 29 in position 8 on the diagram in Fig. 6, in which position the cam 3| at the lower portion of the shaft 28 engages the valve stem 45 and moves the emergency valve 42 from its seat 44 against the bias of the spring 43, thus venting the safety control pipe II to the atmosphere past the valve seat 44 to apply the brakes in a manner to be later described.

If the operator wishes to release the brakes the brake controller handle 29 is moved to its release position, thus reversing the operation of the cams 3i and 32, described above, and interrupting the several circuits closed through conducting segments 33, 34, and 36 of the controller drum 21 in the reverse order to that in which they were closed while the drum was moved to its brake applying position.

If the brakes are applied with the brake controller handle 29 in any service application position, and the rate of retardation of the vehicle becomes sufficient, the pendulum I40 of the retardation controller I2 will swing forward against the bias of the spring I49, pushing the plunger I42 toward the left to cause engagement between its outwardly extending flange I48 and the inwardly extending flange I53 of the sleeve I52, in which position the contact member I44 engages the contact member I45 completing a circuit from the positive terminal of the battery 2I5 through conductor 323, conductor 38I, the contact members I44 and I45 of the retardation controller, conductor 382, to the winding of the magnet I68 in the magnet valve device I3, through conductors 383 and 351 to the negative terminal of the battery 2I5, thus energizing the winding of the magnet valve device I3 and causing the valve I1I to be forced downwardly against the bias of the spring I16 to close communication from the pressure chamber 59 of the brake valve device 6 to the piston chamber I2I of the relay valve device 5 through pipes 6| and I, thus preventing a further increase in pressure within the piston chamber I21 of the relay valve device, and,

consequently, a further increase in pressure within the brake cylinders I and 2.

If the rate of retardation of the vehicle is sulficiently greater than the desired value, the pendulum I40, acting against the plunger I42, forces the plunger I42 and the sleeve I52 to the left, against the bias of the springs I49 and I54, until the contact member I44 engages the contact member I46. Engagement of the contact members I44 and I46 completes a circuit from the positive terminal of the battery 2I5 through conductors 323, 3%", contact members I44, I46, conductor 384, the winding of the magnet I69 in the magnet valve device I 4, conductors 383 and 351 to the negative terminal of the battery 2 I5, thus energizing the magnet of the magnet valve device I4 and forcing the release valve I11 downwardly from its seat to effect communication from piston chamber I2I of the relay valve device 5 to the atmosphere through the application and release pipe 1 and the exhaust port I18, to effect a decrease in the application of the brakes until the retardation controller pendulum I40 interrupts the circuit through the contact member I44 and I46. The setting of the retardation controller I2 may be adjusted, by adjusting the position of the lever I6I operating the cam I58 to effect a rotation of the lever I56 about the pivot pin I51 to press the cap I5I inwardly against the force of the spring I49 to efiect a predetermined compression of the spring, thus requiring particular forces of the pendulum I40 against the plunger I42, to effect the operation of the magnet valve devices I3 and I4.

If, for any reason, the, pressure in the safety control pipe II is lost, or substantially reduced, either by the braking of the pipe, or by the venting of fluid under pressure from the safety control pressure in the safety control pipe 'I I the pressure in the chamber I33 above the piston valve I34 of the deadmans relay valve 9 will be correspondingly reduced, and the pressure below the valve I34 will force the valve from its seat thus venting the piston chamber H1 in the emergency portion of the brake valve device 6 through passage and pipe H8 and the exhaust port I38. The release of fluid under pressure to the atmosphere past the unseated valve I34 will take place at a much more rapid rate than fluid will be supplied to the pipe I I8 from the main reservoir pipe 4I through the choke II9, thus permitting the pistons H6 and I01 together with the block I05 to be moved toward the left by the force of the spring I I4.

As the block I05 moves toward the left the left hand end of the block engages the lower end of the operating lever ml of the brake valve device 6 rotating it in a clockwise direction about the shaft 52 thus moving the plunger 93 toward the right and effecting the supply of fluid under pressure from the main reservoir pipe 4| to the pressure chamber 59 and to the piston chamber I2I of the relay valve device 5 to effect an application of the fluid pressure brakes in the manner above described. Upon movement of the piston I01 toward the left, to the opposite side of the choked port III from that illustrated in Fig. 4, the piston chamber of the sanding relay IIO, which is normally in communication with the atmosphere through passage I09, choke II I, chamber I08 and the exhaust port H2, is connected to the pressure chamber 59 through the passage I09, effecting operation of the sanding valve relay H0.

The closing of the automatic pressure switch 2 I 8 completes a circuit from the positive terminal of the battery 2I5 through conductor 323, the contact members of the switch 2 I 8 and conductor 356, the winding of the track shoe raising magnet valve device I8I, conductor 351 to the negative terminal of the battery 2I5 thus operating the valves 206 and 2I2 downwardly to effect a lowering of the track shoes into engagement with the rail in the manner described above under service application of the brake. The operation of the pressure controlled switch 230 to its circuit closing position completes a circuit from the junction point 358 of the motor circuit through conductor 359, the winding of the track brake line switch 223, conductor 36I tojunction point 362, conductor 386 and the contact members of the pressure operated switch 230 to ground at 381, and to the grounded terminal 331 of the motor, thus applying the counter-electromotive force across the motors 23 and 24 to the winding of the track brake line switch 223 to cause it to operate to its circuit closing position and to remain in that position so long as the vehicle is in motion and the motors 23 and 24 are developing an appreciable counter-electromotive force. The closing of the automatic pressure switch 246 effects the completion of a circuit from the trolley 22I through the conductors of the track raising line switch 223, conductor 224, the contact members of the switch 246, conductor 385, the winding of the relay 229 to ground, thus energizing the winding of the relay 229 and causing it to operate to its circuit closing position. The closing of the relay 229 effects the energization of the winding of the track shoe magnet through conductor 23 I. The circuit completed through the track brake line switch 223 and the relay 229 effects a full energization of the track shoe magnet so long as the vehicle is in motion.

Upon a reduction in pressure in the safety control pipe I I to effect an emergency application of the brakes, the pressure in the piston chamber I66 of the retardation controller I2 is correspondingly reduced permitting the spring I61 to move the piston I65 and the lever I62 to the right, thus increasing the compression of the spring I159 and the force-of the plunger I42 against the pendulum I40. This increases the setting of the retardation controller to effect a rate of retardation of the vehicle during emergency application of the brakes that is greater than the rate of retardation effected during service application of the brakes. The increased setting of the retardation controller requires a greater force of inertia to be exerted by the pendulum I on the plunger I42 to cause engagement of the contact member I44 with the contact members I45 and Means for effecting a deadman application of the brakes comprises the controller handle device 24.5 and the foot valve device 246. If downward pressure is exerted on the handle 252 of the controller handle device 245, and on the foot pedal 214 of the foot valve device 246, urging these levers to their lower or illustrated positions, the chamber 21I of the foot valve device is charged by the flow of fluid under pressure from the safety control pipe I I, through chamber 211 of the cutoff valve device 241, past the unseated diaphragm valve 216, through chamber 218 and pipe 212 to the chamber 21I. Since the lever 214 is in its lower position the diaphragm valve 268 is pressed against the seat rib 269 closing communication between chambers 21I and 261 in the foot valve device. The chamber 261 is charged from the main reservoir pipe 4! through chamber 266 of the pilot valve portion of the controller handle device 245 past the pilot valve 26I in its lower seated position through chamber 263 and pipe 265.

If the operator relieves the pressure on the lever 214 of the foot valve device while maintaining pressure on the handle 252 of the controller handle device the diaphragm valve 268 will be unseated thus connecting the pipe 212 to the pipe 265. Since both these pipes are charged to main reservoir pipe pressure this operation has no effeet on the brake system. If, while maintaining pressure on the lever 214 ,of the foot valve device, pressure is released from the handle 252 of the controller handle device the pilot valve 26I will be moved upwardly to its upper seated position by 'ber 266.

action of the spring 256, which will move the pin 255 downwardly against the left hand end of the lever 251, thus venting the pipe 265 through chamber 263 and the exhaust port 264, and closing communication from the main reservoir pipe Al to the pipe 265 through the pilot valve cham- This action is also ineffective to vent the safety control pipe II since communication between the controller handle device 245 and the safety control pipe is closed by the foot valve device 246.

Should,'however, the operator release pressure from both the foot valve lever 214 and the controller handle 252 at the same time, fluid would be vented from the safety control pipe I I, through chambers 211 and 218 of the cut-off valve device 241, through pipe 212, past the unseated valve 268 of the foot valve device, through pipe 265, the pilot valve chamber 263 and the exhaust port 264 to the atmosphere, thus effecting an emergency application of the brakes in the manner above described. As the brake cylinder pressure builds up, fluid under pressure flows from the brake cylinder pipe I26 to the chamber 281 in the cut-off valve device until the pressure below the valve 282 has become sufficient to move the valve upwardly to its upper seat 285 against the force of the spring 284, thus closing communication from the chamber 28I to the atmosphere and effecting a pressure within the chamber 28I corresponding to brake cylinder pressure to force the diaphragm 219 and the valve 216 downwardly to cut off communication between the safety control pipe II and the pipe 212. The cut-off valve device 241 is adjusted to operate to close communication between the safety control pipe I I and the pipe 212 upon brake cylinder pressure corresponding to a moderate service application. The operator may, therefore, after effecting such a service application of the brakes, relieve pressure from both the handle 252 of the controller handle device and the lever 214 of the foot valve device without effecting an emergency application of the brakes.

The check Valve device 213 prevents the venting of air from the safety control pipe I I through the deadman devices including foot valve device 246 and the controller handle device 245 after the pressure in the brake cylinder pipe I26 has built up sufliciently to cause the diaphragm valve 216 of the cutoff valve device 241 to be forced to its seat, thus closing communication between the safety control pipe II and the pipe 212, while permitting the safety control pipe I I to be charged with fluid under pressure from the main reservoir pipe 4| through chambers 266 and 263 i in the pilot valve device, past pilot valve 26! when the handle 252 of the controller handle device 245 is in its lower position, through pipes 265 and 212 and check valve 213 when the diaphragm valve 268 of the foot valve device is unseated.

While one preferred embodiment of my in vention has been illustrated and described it will be apparent to those skilled in the art that many modifications in the apparatus and circuits illustrated may be made within the spirit of my invention and I do not wish to be limited otherwise than by the scope of the appended claims.

Having now described my invention, what I claim as new and desire to secure by Letters Patent, is:

1. In a brake equipment for vehicles, in combination, a brake cylinder, an electric brake, manually operable means for controlling the supply of fluid under pressure to said brake cylinder and for controlling said electric brake, a retardation controller responsive to the rate of deceleration of the vehicle for regulating the degree of fluid pressure in said brake cylinder, and manually operable means independent of said brake controlling means for varying the setting of said retardation controller under service conditions.

2. In a braking equipment for vehicles, in combination, fluid pressure braking means, magnet track braking means, dynamic braking means, manual means for controlling the application and release of said several braking means and effective upon movement from its release position to effect in sequence a gradual application of the fluid pressure braking means to a predetermined value, a gradual application of the magnetic braking means, a further gradual application of the fluid pressure braking means, and an application of the dynamic braking means in the order named.

3. In a brake equipment for vehicles, in combination, fluid pressure braking means, magnetic track braking means, dynamic braking means, manually operable means for controlling the application of said several braking means and effective upon movement away from its release position to effect in sequence, a gradual application of the fluid pressure braking means to a predetermined value, a gradual application of the magnetic braking means, a gradual further application of the fluid pressure braking means, an application of the dynamic braking means, and an emergency application of said brakes.

4. In a brake equipment for vehicles, in combination, fluid pressure braking means, magnetic track braking means, dynamic braking means, manually operable means for controlling the application of said several braking means effective upon movement from its release position to eflect a gradual application of the fluid pressure braking means to a predetermined value, a gradual application of the magnetic braking means, an application of the dynamic braking means, and an emergency application of said brakes in the order named.

5. In a brake equipment for vehicles, in combination, a fluid pressure braking means, magnetic track braking means, dynamic braking means, manually operable means for controlling the application and release of said several braking means and effective upon movement from its release position to effect a graduated application of the fluid pressure braking means to a predetermined value, a graduated application of the magnetic braking means, and an application of the dynamic braking means in the order named.

6. In a brake equipment for vehicles, in combination, a fluid pressure braking means, magnetic track braking means, dynamic braking means, manually operable means for controlling the application of said several braking means, effective upon movement from its release position to effect a gradual application of the fluid pressure braking means to a predetermined value, a gradual application of the magnetic braking means, a gradual further application of the fluid pressure braking means, and an application of the dynamic braking means in the order named, and a retardation controller responsive to the rate of deceleration of the vehicle for controlling the degree of application of said fluid pressure braking means.

7. In a brake equipment for vehicles arranged to be propelled by electric motors and having an electric controller for controlling the supply of power to the motors,in combination, a fluid pressure brake, an electric brake, manually operable brake controlling means for controlling the application and release of said fluid pressure brake and said electric brake, and means effective upon movement of said manually operable brake controlling means to any brake applying position for interrupting the flow of power to said electric motors independently of the position of the electric controller.

8. In a brake equipment for vehicles, in combination, a fluid pressure braking means, an electric braking means, manually operable means for controlling the application and release of said braking means, a safety control pipe normally charged with fluid under pressure, and a plurality of separate means associated respectively with each of said braking means and independently responsive to the release of fluid under pressure from said safety control pipe for effecting an emergency application of the brakes.

9. In a brake equipment for vehicles, in combination, a fluid pressure braking means, an electric braking means, manually operable means for controlling the application and release of said braking means, a safety control pipe normally charged with fluid under pressure, a plurality of means each independently responsive to the release of fluid under pressure from said safety control pipe for efiecting an emergency application of the several braking means, and deadman devices subject to pressure by the operator and operative upon the release of such pressure for venting fluid under pressure from said safety control pipe.

10. In a brake equipment for vehicles, in combination, a. fluid pressure braking means, an electric braking means, manually operable means for controlling the application and release of said braking means, a safety control pipe normally charged with fluid under pressure, means responsive to the venting of fluid under pressure from said safety control pipe for effecting an emergency application of the fluid pressure braking means, and a plurality of independent means separately responsive to the Venting; of fluid under pressure from said safety control pipe for effecting an emergency application of the electric braking means, deadman devices subject to pressure by the operator and operative upon the release of such pressure for venting fluid under pressure from the safety control pipe, and means effective upon a predetermined service application of the brakes for preventing the release of fluid under pressure from said safety control pipe through said deadman devices.

11. In a brake equipment for vehicles, in combination, a fluid pressure braking means, an

electric braking means, manually operable means for controlling the application and release of said braking means, a safety control pipe normally charged with fluid under pressure, a plurality of separate means associated respectively with each of said braking means and independently responsive to the venting of fluid under pressure from said safety control pipe for eiiecting an emergency application of the brakes, and a plurality of means for effecting the release of fluid under pressure from said safety control pipe.

12. In a brake equipment for vehicles, in combination, a brake cylinder, an electric braking means, manually operable means for controlling the supply of fluid under pressure to said brake cylinder and for controlling the application and release of said electric braking means, a safety control pipe normally charged with fluid under pressure, means responsive to a reduction in safety control pipe pressure for causing fluid under pressure to be supplied to said brake cylinder to effect an emergency operation thereof, and an electric circuit closing means responsive to a reduction in safety control pipe pressure for eifecting an emergency application of said electric braking means.

13. In a brake equipment for vehicles, in combination, a brake cylinder, electric track shoe braking means, manually operable means for controlling the supply of fluid under pressure to said brake cylinder and the application and release of said track shoe braking means, a safety control pipe normally charged with fluid under pressure, means responsive to a reduction in safety control pipe pressure for effecting the sup ply of fluid under pressure tosaid brake cylinder, and electric circuit closing means responsive to a reduction in safety control pipe pressure for effecting an emergency application of said track shoe braking means, and means responsive to the stopping of the vehicle for automatically releasing said track shoe braking means.

14. In a braking equipment for vehicles, in combination, a fluid pressure braking means, an electrical braking means, manually operable means for. controlling the application and release of said several braking means, a retardation controller responsive to the rate of deceleration of the vehicle for regulatirr the degree of appli cation of said braking means, means manually operable at the will of the operator for adjusting the setting of said retardation controller, to effect a desired rate of retardation of the vehicle during service application of the brakes, and means automatically operable to vary the setting of said retardation controller to elfect an increase in the rate of retardation of the vehicle upon an emergency application of the brakes.

15. In a braking equipment for vehicles, in combination, a brake cylinder, a magnetic track brake, manually operable means for controlling the supply of fluid, under pressure to said brake cylinder and the degree of application and release of said track brake, a retardation controller responsive to the rate of deceleration of the vehicle for regulating the degree of fluid pressure in said brake cylinder, manual means operable at the will of the operator independently of the application of the brakes for adjusting the setting of said retardation controller to effect a desired rate of retardation of the vehicle during service application of the brakes, and means automatically operable to vary the setting of said retardation controller to effect an increase in the rate of retardation of the vehicle by a fixed amount upon an emergency operation of said brakes.

16. In a braking equipment for vehicles, in com bination, a fluid pressure braking means, an electrically operated braking means, manually operable means for controlling the application and release of said several braking means, a retardation controller responsive to the rate of deceleration of the vehicle for regulating the degree of application of one of said braking means, a safety control pipe, and means eflective upon a reduction in safety control pipe pressure for effecting an emergency operation of said brakes and for automatically increasing the rate of retardation of the vehicle permitted by said retardation controller by a fixed amount above its service rate of retardation.

17. In a braking equipment for vehicles, in combination, a fluid pressure braking means, a plurality of electrically energized braking means, manually operable means for controlling the application and release of said several braking means, and means responsive to the ceasing rotation of the vehicle Wheels for releasing said electrically energized braking means independently of V the operation of said manually operable means.

18. In a brake equipment for vehicles, in combination, fluid pressure braking means, magnetic track braking means, dynamic braking means, manually operable means for controlling the ap plication of said several braking means and effective upon movement from its release position to effect an application of the dynamic braking means, a gradual application of the fluid pressure braking means, a gradual application of the magnetic braking means, and a gradual further application of the fluid pressure braking means, and a retardation controller responsive to the rate of deceleration of the vehicle for controlling the degree of application of said fluid pressure braking means.

19. In a brake equipment for vehicles, in combination, a fluid pressure braking means, magnetic track braking means, dynamic braking means, manually operable means for controlling the application of said several braking means effective upon movement from its release position to eifect a gradual application of the fluid pressure braking means, a gradual application of the magnetic braking means, a gradual further application of the fluid pressure braking means, and an application of the dynamic braking means within the fluid pressure service application zone, and a retardation controller responsive to the rate of deceleration of the vehicles for controlling the degree of application of said fluid pressure braking means.

20. In a brake equipment for vehicles, in combination, a fluid pressure braking means, magnetic track braking means, manually operable means for controlling the application of said several braking means effective upon movement from its release position to effect a gradual application of the fluid pressure braking means, a gradual application of the magnetic braking means, and a gradual further application of the fluid pressure braking means, and a retardation controller responsive to the rate of deceleration of the vehicle for controlling the degree of application of said fluid pressure braking means.

21. In a brake equipment for vehicles, in combination, a fluid pressure braking means, magnetic track braking means, manually operable means for controlling the application of said several braking means effective upon movement from its release position to effect a gradual application of the fluid pressure braking means and a gradual application of the magnetic braking means, said magnetic braking means being arranged to be applied in a series of steps, the first step occurring substantially after the initial application of said fluid pressure braking means and the last step occurring substantially prior to the completion of the application of the fluid pressure braking means, and a retardation controller responsive to the rate of deceleration of the vehicle for controlling the degree of application of said fluid pressure braking means.

22. In a braking equipment for vehicles, in combination, a fluid pressure braking means, an electrically energized track shoe braking means, a

dynamic braking means, manually operable means for controlling the application and release of the several braking means, and means responsive to a decrease in the rotation of the vehicle wheels to a predetermined value for interrupting the energization of said track shoe braking means independently of the operation of said manually operable means.

23. In a braking equipment for vehicles, in combination, a fluid pressure braking means, an electrically energized track shoe braking means, electric generator braking means for applying a braking force to the vehicle wheels, manually operable means for controlling the application and release of the several braking means, and means responsive to the decrease in the braking force of said generator braking means to a predetermined value for interrupting the energization of said track shoe braking means independently of the operation of the said manually operable means..

24. In a vehicle brake system, in combination, a magnetic track brake device normally suspended above a track rail, a pipe normally charged with fluid under pressure, automatic control switch means connected to said pipe and having associated contacts adapted to be operated when the pressure in said pipe is diminished, means responsive to operation of certain of said contacts for effecting a supply of current to said track brake device, and means responsive to operation of other of said contacts for effecting lowering of said track brake device to engagement with the track rail.

25. In a vehicle brake system, in combination, a magnetic track brake device adapted to be normally suspended above a track rail, a circuit for supplying current to energize the track brake device, a resistance in said circuit, a pipe normally charged with fluid under pressure, three automatic control switch devices connected to said pipe each of which is adapted to close contacts therein when pressure in said pipe .is diminished, means responsive to the closing of the contacts in one of said switch devices for connecting said circuit to a source of current supply, means responsive to the closing of the contacts in another of said switch devices for effecting shunting of said resistance in said circuit, and means responsive to the closing of the contacts in the last of said switch devices for effecting lowering of said track brake device to engagement with the track rail.

26. In a vehicle brake system, in combination, a magnetic track brake device, fluid pressure operated means adapted when fluid under pressure is supplied thereto for holding said track brake device suspended above a track rail, a pipe normally charged with fluid under pressure, a switch device connected to said pipe and having contacts therein adapted to be operated when the pressure in said pipe is diminished, and means responsive to said operation of said contacts for releasing fluid under pressure in said fluid pressure operated means.

2'7. In a vehicle brake system, in combination, a magnetic track brake device, fluid pressure operated means adapted when fluid under pressure is supplied thereto to maintain said track brake device suspended above a track rail, and adapted when fluid under pressure is released therefrom to permit said track brake device to drop by gravity to engagement with the track rail, a pipe normally charged with fluid under pressure, a first and a second switch device connected to said pipe, each of said switch devices having contacts therein adapted to be operated when the pressure in said pipe is diminished, means responsive to the operation of the contacts in said first switch device for effecting a release of fluid under pressure from said fluid pressure operated means, and means responsive to the operation of the contacts in said second switch device for effecting a supply of current to said track brake device.

28. In a vehicle brake system, in combination, a magnetic track brake device, fluid pressure operated means adapted when fluid under pressure is supplied thereto to maintain said track brake device suspended above a track rail, a magnet valve device adapted when current is supplied thereto to effect a release of fluid under pressure from said fluid pressure operated means, a pipe normally charged with fluid under pressure, and a switch device connected to said pipe for controlling the supply of current to' said magnet valve device.

29. In a vehicle brake system, in combination, a magnetic track brake device, fluid pressure operated means adapted when fluid under pressure is supplied thereto for holding said track brake device suspended above the track rail, a pipe normally charged with fluid under pressure, and means responsive to a reduction in pressure in said pipe for releasing fluid under pressure from said fluid pressure operated means and for causing the energization of said track shoe to effect an emergency application of said magnetic track shoe braking means.

ELLIS E. HEWITT. 

